Engine governing system



Feb. 16, 1937.

J. L. TAYLOR ENGINE GOVERNING SYSTEM Filed Feb. 27, 1932 2 Sheets-Sheet l ATTORNEY.

INVENTOR:

JZJZm Leonaraic'zy/ar:

Feb. 16, 1937. J. L, TAYLOR ENGINE GOVERNING SYSTEM Filed Feb. 27, 1932 2 Sheets-Sheet 2 INVENTOR: JZJfi/z [wizard 7451/01.

ATTORNEY.

.33 33' fie. 8.

Patented Feb. 16, 1937 UNITED STATES PATENT OFFICE 7 Claims.

This invention relates to engines, and particularly to governing means therefor, and an object of the invention is to provide for the general im provement of the construction and operation of apparatus of this class.

A further object is to provide improved fuel injecting means for a combustion engine.

A further object is to provide such means having improved means for regulating the amount of fluid injected. e

A further object is to provide injecting means comprising generally a variable stroke pump.

A further object is to provide improved mechanism for varying the stroke of said pump.

A further object is to provide such mechanism including a wedge element.

A further object is to provide such a wedge mechanism having an exceptionally large range of movement.

A further object is to provide improved connections between said mechanism and said pump.

A further object is to prevent sticking of said wedge mechanism.

.A further object is to provide improved speed responsive mechanism for operating said wedge mechanism.

A further object is to provide improved connections between said speed responsive mechanism and said wedge mechanism.

A further object is to provide manually operable means for modifying the action of said speed responsive means.

A further object is to provide means for manually taking over the control of the wedge mechanism, and accordingly of the engine.

A further object is to provide an improved variable stroke injection pump.

A further object is to provide for bleeding undesired substances from said pump.

A further object is to provide for recovering or disposing of normal leakage in said pump.

A further object is to provide improvements in the details of the mechanism of the various units in the apparatus, in the interests of compactness, efficiency, and economy of materials and in manufacture.

Further objects and advantages will become apparent from the following specification, in which:

Fig. 1 is a transverse sectional elevation through an engine block with certain parts beyond the section-plane, removed.

Fig. 2 is a section on line 2-2 of Fig. 1.

Fig. 3 is a fragmentary view of Fig. 1 looking in the opposite direction.

Fig. 4 is a fragmentary top-plan of Fig. 3.,

Fig. 5 is a fragmentary perspective of a wedge mechanism employed in this invention.

Figs. 6, '7, and 9 are perspective details of parts of this invention.

Fig. 8 is a section on line 8-8 of Fig. 1.

Fig. 10 is a fragmentary detail of a guide bushing element employed.

Fig. 11 is a. modification of the wedge means seen in Fig. 5. 7

Similar characters of reference apply to like parts throughout the several views.

The character E indicates the top or table surface of an engine block whereon the several con trol features, employed in engines of this type, may conveniently be located. Fig. 1 illustrates a group of control elements which will be understood to be repeated in all respects except for the governor assembly G as many times as there are engine cylinders, in the present instance there, being a plurality of cylinders CL and GL However, all of these groups will be served in the present instance by a single governor means particularly arranged to automatically regulate the functions of said control elements. .25

An injector pump body assembly B extends above and below the table top E, the lower portion being labeled B. Within the body BB" reciprocates a fluid injector pump piston or plunger I, Fig. 2, in the present instance embraced by a lifter assembly L which latter is reciprocable in the said pump assembly, and a tappet assembly comprising a guide member 2 in the present instance downwardly urged by a spring 3 to cause reciprocation of said member, within the portion B, under the influence upon a roller R of a cam C, the latter being suitably fixed upon a camshaft S.

Lifter L comprises a ring base 4 having fixed therewith a sleeve or stop member 5, and a stem 6, said stem having a guide or sleeve 1 adjustably fixed therewith and provided with suitable locking means such as a set-screw 8. The pump body B is apertured to provide a cylinder bore 9, and both portions B and B are similarly enlarged at Bb to provide room for the movement of base 4, and its offset stem 6, and also for a spring I 0 the function of which is to downwardly urge the aforesaid lifter. The portion B is divided by a suitable 50 partition at b having a centering bore for the sleeve or stop 5 and also to provide a stop for downward movement of the lifter L. The sleeve 5 is open at its bottom but provided with a shoulder I I upon which rests, after the outward stroke 55 of plunger 1 an enlarged flange i fixed with the plunger a short distance from its lower end.

The guide member 2 is arranged to provide a piston actuating pad or tappet 2' about which pad is arranged a spring I2 that seats against partition 17 and urges the roller and cam into substantially continuous contact. In the bore of the body portion B is arranged a piston-guide bushing or liner [3 having an enlarged flange l3 providing an abutment for a piston spring Hi whose opposite end seats against the flange I to urge piston l downwardly in opposition to cam C insofar as the piston is permitted to travel by the position of lifter L. The piston is raisedto a predetermined position upon each reciprocation of guide 2 by contact of tappet 2' with end portion I, and is then moved downwardly by spring M to a point determined by the position of lifter L. The stroke of the piston is accordingly determined, by the vertical position of lifter L. The piston l is accurately centered in the bore 9 by sliding fits respectively provided its flange and stem portions'in theguide and guide bushing l3.

Fluid is supplied the said pump assembly by a tube T divided at each pump unit to accommodate a valve fitting V. (This fitting is fully'illustrated, described and claimed in my co-pending application filed September 26, 1931, Serial No. 565,282.) Beneath the valve V the body B is'ported to discharge the fluid through a tube T leading to an atomizer unit A, Fig. 1, generally located in the present instance between suitable housings H extending above the top E, the said housings in the present instance accommodating scavenging valves operated by tappet rockers K. The fulcrum. of said rockers in the construction illustrated is a hollow shaft [4 having slots i l formed therein and within the said shaft is disposed a co-axial and oscillatable governor rod l5 from which depends a stud 86 that is rigidly fixed with the rod and carries a bifurcated block or abutment I! which, in turn, bears against a slotted pivot-carrying plate or member 18 located on the end of a stem [9 which is reciprocable in a suitable bore 20 formed in one of the housings H, and outwardly thrust by a spring 2! bearing against the said plate 18.

The body B has a recess ba formed in a side thereof defined between the enlarged portion of body'portion B and a lug bb, the latter being bored and suitably finished to provide a correct and true bearing for the reciprocable guide or sleeve 1. Within this recess ha is positioned in the present instance a series of alternately arranged forked wedges 22, and apertured wedges 23, which receive the stem 6 as a guide therethrough. The uppermost wedge 23' has a flat surface plane so disposed as to be at substantially right angles to said stem 6 and upon which the said guide sleeve 1 is screwed down to insure a precisely determined position of the lifter base 4 relatively to the wedge 23'. When this position has been satisfactorily determined, the sleeve 1 is locked by jamming the set-screw 8 against the end of the stem 8.

The apertured wedges 23 are stationary about the stem 6 and lie parallel to and may abut the inner wall of the recess bar, while the wedges 22,

being forked, are free to slide in and out on guideways 23a, Fig. 5, formed in the present instance on opposite faces of the Wedges 23, wedges 22 being moved by virtue of links 24 which are in the presentinstance articulately pinned to the wedges 22 and to the plate l8. Fig. 5 illustrates the general aspects of the Wedge elements, and shows the forked wedges 22 provided with shallow grooves or scores 22 which prevent a vacuum from occurring between their sliding faces, and assist in avoiding cohesion of the wedges and sticking of the governing mechanism. With the foregoing arrangement the spring 2| Fig. 1 tends to thrust the wedges 22 between the wedges 23 which action tends to raise the sleeve 7 and with it the lifter assembly L, thus raising the point at which the flange l contacts the shoulder l l and shortening the stroke of plunger 1. The withdrawal of the wedges 22 is obtained through the oscillations of the rod i 5, which, through the rigidly connected block 11 abutting against the plate l8, opposes the spring 2 I.

There is normally a small amount of leakage, foam, and entrapped air or the like occurring in the pump means before described which requires consideration. The bore 9 is provided with a bleeder-valve 26 whose function is to allow the escape of aerated fluid, as in starting, and at other times later if and when the accumulation of air or other material is discovered to be interfering with atomizer operation. A small amount of fluid will also find its way, as leakage, down the piston l and this is cared for inthe bushing sleeve i3 where an annular oil well wiper groove 21, about the sleeve bore, leads to a suitablepassage such as groove 28 in the body B, which latter is drained by a tube 29 that carries the aerated fluid or leakage to a suitable receptacle. The discharge from valve 26 is connected as shown in the present instance to tube 29. v t

The camshaft S is actuated, in the present instance, through appropriate driving and driven gears, respectively 3! and 32, Fig. 1, by a governor shaft 33 which, in turn, is operated from the engines crankshaft 33a through spiral or other suitable gears 33b and 330 respectively on the crankshaft and governor shaft. The said governor shaft is in the present instance in two portions, the lowerportion 33 being axially bored to receive the upper portion 33', the said lower portion extending upward as a sleeve to receive the gear 3| fixed thereto, while the upper portion or inner shaft 33' will upwardly extend into a swivel connection including in the present instance a cup 34, as more particularly shown in i Fig. 3, where its end terminates in a thrust bearing 35 within said cup. A threaded stud 36 is provided with an enlarged head 31 in the present instance screwed into the aforesaid cup which leaves the said stud axially aligned with the gov ernor shaft 33.

Concentrically about the aforesaid cup is a tubular shell or guide 38, depending from the table E, within which is slidably positioned a springcage 39 within which is a spring 46, surrounding the cup 34 and acting between a lower portion of spring cage 39 and a disk 4| through which it acts on stud 36, as will presently appear. The stud 36 is held non-rotatively by means of a washer 42 that fits over an enlarged and flattened root portion of said stud above head portion 31, said washer having opposed lugs 42' disposed in depressions formed in the cups brim. The position of the disc 4| is fixed relatively to stud 36 by a coned nut 43 threaded upon said stud and the latter extends upwardly to receive an actuating member 44', rigidly attached to said stud in the present instance and having a vertical leg forming a rack 44 in mesh with a pinion 45 keyed t t e end of rod l5. Other means might be provided to convert the linear movement of stud 36 into rotative movement in rod l5 within the contemplation of the present invention.

The end bearing 46 for said rod provides a guide way 41 wherein slides the aforesaid actuating member. The spring-cage 39 is provided with trunnions 48, Fig. 1, which are engaged by a manually adjustable fork 49 whose pivot shaft 59 is rotatable by virtue of a worm gear segment 5!, Fig. 3, fixed therewith and in mesh with a worm 52 which latter is, in turn, fixed with a control shaft 53 which leads to a hand-wheel or the like not shown accessibly disposed outside the engine block for affecting the spring 40. The latter functions in opposition to the aforesaid governor assembly G and by increasing or decreasing the stress in spring 46 by raising or lowering cage 39 through operation of the hand-wheel, the speed at which the governor will overcome the spring, and accordingly the speed which it will maintain at the engine may be varied.

In the event that it is desired to control the engine manually, this may be done by a lever 59, Fig. 4, pivoted on a screw or the like a: fixed with rack portion M, the lever having a cam extension or abutment portion 59' engaging a stud 6f! fixed in the present instance with a bolt 6! fixed with bearing member 46. Movement of lever 59 in one direction will depress rack 44 in opposition to spring 40, and thus control the injection pumps and accordingly the engine independently of the governor. With spring 40 adjusted for a maximum speed, the lever gives a full control of the engine analogous to a hand throttle. The lever may also be set to positively limit the stroke of the injection pumps when desired, as in starting and in certain kinds of service. When the control of the engine is taken over by lever 59, the governor still remains on guard, as it were, and operates to limit the engine speed in the event of failure of load, or the like, to that for which spring fill is adjusted. Hand control is thus possible without danger of a run-away.

Governor assembly G is generally of the centrifugal type, and includes a body portion 54 fixed with governor shaft portion 33 and having wing portions 54' extending outwardly and upwardly therefrom at either side of a member 55 slidable on shaft 33 in a region above body portion 54, and provided with slots 55, and an upwardly extending sleeve portion 55". A pin 56 engaged with said sleeve portion extends through slots 5? in shaft portion 33 and actuates shaft portion which, as above described extends downwardly in the bore of the hollow portion of shaft 33. Governor weights 58 are suitably pivoted to wings 54 opposite slots 55 and have tongues 58' engaging the slots, the weights swinging outwardly under centrifugal force as indicated by the dotted lines, and depressing member 55 and shaft 33 in opposition to spring 40. Each of tongues 58' is inclined downwardly relatively to its slot 55 in allpositions of the part whereby it travels in an arc, producing the effect of a variable horizontal lever arm about its pivot,

in the present instance decreasing in effective length as the weights 58 respond to centrifugal force, so that the product of the said lever arm and weight force will change with speed changes at nearly the same rate as the changes in opposing force caused by the compression of spring d5 due to the linear movement of sleeve 55". The governor is thus given a wider range of movement for a given speed change than prior structures of this general type.

The operation of the above described mechanism is as follows:

The rotation of the engine crankshaft (not shown) rotates governor shaft 33, which, thr0ugh gears 3i, and '32 rotates cam shaft S at a rate such as to produce a stroke of each of the in jection pump plungers i for each working stroke or cycle of their respective cylinders. This rotation causes a regular reciprocation of guide member 2 in portion B, roller R following cam C under the pressure of spring 3. Plunger i forced downwardly by spring M to the extent permitted by lifter L is contacted by tappet 2 upon each upward movement of member 2, and raises plunger to a predetermined upper limit of its stroke. Upon downward movement of member 2, plunger I follows it to the position determined by lifter L, where it remains suspended pending the next upward movement of member 2. The effective stroke of plunger l, is accordingly the difference between the predetermined upper position aforesaid and the lower position deter mined by lifter L. Change of position of the lifter will accordingly change the stroke, upward movement thereof shortening it, and downward movement lengthening it. The range of move ment of lifter L may be made such as to control the Whole of the possible movement of plunger" I. and may if desired be arranged to be capable of raising the plunger above the range of movement of tappet 2', so that there will be no stroke of the plunger, and accordingly no injection of fluid by the pump.

Downward movement of plunger I draws fluid into bore 9 through valve fitting V, while upward movement thereof expels the fluid through tube T to the injection nozzle A. Emulsified fluid or thelike may be discharged through bleeder valve 26, and leakage past the plunger is recovered by a tube 2%. The amount of fluid delivered by the pump for each injection is determined by the stroke of plunger 5. and this is determined by the position of litter L as outlined above, and this position is in turn determined by the governing apparatus as follows:

Governor weights 58 in moving outwardly under centrifugal force operate through member 55 to depress governor shaft 33, and the shaft,

through swivel connection 34, moves rack portion {14 downwardly. thus rotating rod iii in a clockwise direction as seen in Fig. 1. This movement of rod 15 moves member l? to the left, and permits spring 2| to force wedges 22 further into the spaces between wedges 23. This movement of the wedges has the effect of raising wedge 23 and with it sleeve member '5. Member I. being fixed with stem 6, raises also the stem and portion of lifter L, thus shortening the stroke of plunger I. as above described. The amount of fluid injected into the engine cylinder is accordingly reducedand the excessive speed that caused the outward movement of the governor weights is checked.

If the speed becomes too slow. the spring 40 overcomes the reduced centrifugal force in weights 58, and forces shaft 33' upwardly, reversing the movement of the parts just outlined. Member from between wedges 23 to a certain extent, against the force of spring 2!, thus allowing lifter L to fall and increasing the stroke of pump plunger This increases the volume of fluid injected and restores the speed to that for which the spring 40 is adjusted.

The use of a spring 2| for forcing the wedges I? then acts to withdraw wedges 22' 22 between wedges 23 and 23 is desirable for the reason that plunger I, through collar I is resting during the major portion of the time on carrier 4, and forcing of the wedges 22 in this direction under such conditions would require raising the carrier as above explained, which would in turn raise the plunger, and since the upward movement of the plunger is the active, or pumping stroke thereof, this movement has to be made against the full fluid pressure for which the nozzle A is intended. There would be no j-ustification for making the governor mechanism powerful enough to do this, and furthermore, it is undesirable to have a pumping stroke of plunger l occur at any time except when caused by cam C. At this moment, however, relatively little force is required to move the wedges in the direction to raise carrier 4 against the resistance of spring In, the carrier being relieved of the load of plunger I by the action of the cam. Yoke l1 having previously been moved away from member l8 by the action of the governor, spring 2| readily moves the wedges to the extent permitted by the position of yoke l1 during the interval that plunger I is raised by the cam C.

In a single cylinder engine, this movement might be satisfactorily performed by the direct action of the governor during this time, but if there is more than one cylinder, it will be seen that the pumping impulses will be successive, and since they are short, they will not overlap. Consequently, during the interval that any plunger is raised by its cam, at least one other plunger will be resting on its carrier 4, and offering such resistance to the movement of the wedges as to prevent actuation by the governor. The spring construction disclosed prevents this difficulty, the wedges associated with the various cylinders being forced in successively after a change in governor position during the first pumping cycle after the change. Obviously the above difficulty is not present in the event of a change in the direction to withdraw the wedges 22 from between wedges 23 and 23 since the movement of the plungers is then in the direction of a suction, and not a delivery stroke, and the springs l0 and I4 tend to assist, rather than prevent the action of the governor.

If a change of speed is desired it can be effected by adjusting the force of spring 40 by means of the hand-wheel or the like on shaft 53, and if hand control of the engine is required, it can be had by manipulating lever 59. In practice when a hand control is required, spring 40 would be adjusted for a maximum permissible speed of the engine, and the control effected by lever 59, the engine still being under governor control in the event of failure of load or the like.

It is desirable that the mechanism responsive to governor weights 58 operate as freely as possible, and as an alternative expedient to the grooves 22 of Fig. 5, to reduce friction or cohesion of the wedges, they may be provided with anti-friction means as suggested in Fig. 11. In this construction the wedges 23m are provided with suitable grooves in which are disposed balls 23a: or other suitable anti-friction members which will result in a rolling rather than a sliding contact between the wedges 23m and 22m. In thisembodiment the grooves 22 are omitted, and the wedges 22m are finished with plane faces to serve as races for the balls 23m.

The parts are so arranged that all necessary adjustments can be readily made. For example, the stroke of any pump plunger I can be adjusted relatively to other pump plungers on a given engine by changing the setting of sleeve 1 until the engine indicates that the correct amount of fluid is being injected into the particular cylinder affected. This adjustment can be made very accurately, and positively maintained by tightening set screw 8. Likewise, the relative position of wedges 23 and the governor weights 58 can be changed by adjusting nut 43 up or down on stud 36. In this manner the governor weights can be made to maintain various positons for a given load on the engine, and any advantages which might flow from such a change can be realized.

Numerous advantages are attributable to the particular arrangement of the parts of the device. Some of these will be enumerated, but it is to be understood that the invention is not limited to such as are mentioned, but embraces any and all advantages that may be realized by the disclosed structure, or any variation thereof within the province of one skilled in the art, and that the invention is not to be taken as limited by anything disclosed in the above illustrative embodiment, or in fact in any manner except as defined in the annexed claims.

In addition to the above described operative advantages, the structure is unusually compact and light in weight because of the inclusion of the governor rod l5 in the hollow fulcrum l4 of the tappet rockers K. Similar advantages are apparent from the driving of the cam-shaft from the governor shaft 33. The cam-shaft is thus readily located high up in the engine, so that the individual injection pumps can be located adjacent to their respective spray valves, and the passages thereto can be extremely short and direct, and such parts as occasionally need adjustment are located on top of the engine where they are readily accessible.

Having described the invention What is claimed and desired to protect by United States patent 1. In an engine the combination of a plurality of cylinders, a crank shaft, and a cam shaft, said cylinders being provided with mechanism operated from said cam shaft, tappet rockers arranged to operate said mechanism, a common fulcrum for said rockers including a hollow rod on which said rockers are journaled, fuel regulating means individual to the respective cylinders, a speed responsive device driven from said crank shaft, and connections from said speed responsive device to said fuel regulating means including a rod extending into said common fulcrum, and elements projecting from said rod through suitable openings in the walls of said fulcrum and connected to operate said individual fuel regulating means upon movement of said rod in response to changes in the position of said speed responsive device.

2. In a governing system for an engine the combination of a crank shaft and a fuel regulating device, an upwardly extending governor shaft connected to be driven from said crank shaft, said shaft being hollow and having an extension slidable in the bore thereof and projecting above the upper end of said shaft, a speed responsive device on said governor shaft between the ends thereof, and a connection extending through the wall of said governor shaft and arranged to slide said extension in response to movements of said speed responsive device,

and other connections from the projecting portion of said extension arranged to actuate said fuel regulating device, whereby said governor shaft may transmit power between a point below and a point above said speed responsive device.

3. In a fuel pump structure the combination of a pump plunger having a variable stroke, resilient means urging said plunger in one direction, and reciprocating means arranged to actuate said plunger in the other direction, stop mechanism movable for determining the extent of movement effected by said resilient means whereby to determine the return stroke effected by said reciprocating means, and means for positioning said stop means including a plurality of superimposed wedges, alternate wedges being constrained to move only in the direction of movement of said stop means, and the remaining wedges being free to move in the direction of movement of said stop means, and also in a direction transverse to the direction of said stop means, and a control device arranged to move the last mentioned wedges in said transverse direction, the lowermost of said wedges being supported on a fixed element, and the uppermost engaging a portion of said stop mechanism, whereby rising or falling movement of said uppermost wedge caused by said transverse movement of said remaining wedges will cause movement of said stop mechanism.

4. An engine governing system including a speed responsive device, a fuel pump including a piston, stop means for determining the stroke of said piston, and means for reciprocating said piston, a vertically adjustable stem member connected with said stop means for positioning it in accordance with the vertical position of said stem, and means actuated from said speed responsive device for positioning said stern including a plurality of interfitting superposed Wedge blocks, fixed means for supporting the lowermost of said wedge blocks, and means connecting the uppermost of said wedge. blocks with said stem, whereby rising and falling movement of said wedge block will be communicated to said stem, alternate wedge blocks being apertured and guided on said stem, and the remaining wedge blocks being slotted and capable of movement transverse to the direction of movement of said stem, and connections from said speed responsive device for so moving the last mentioned wedge blocks.

5. In a governing device for a combustion engine the combination with fuel injecting means including a pump, a reciprocating member driven from said engine, and a plunger for said pump positioned to be driven from said member, a yieldable element arranged to actuate said plunger in one direction, said plunger being actuated in the other direction by said reciprocating member in opposition to said yieldable element, stop means limiting the movement of said plunger in the direction actuated by said yieldable element, means operative to determine the position of said stop means including a speed responsive device, and a spring opposing the action of said device, of means for adjusting the force exerted by said spring whereby to change the characteristics of the action of said speed responsive device, and

a hand control for positioning said stop means including a manually operable member arranged to over-come said spring and determine a maximum stroke of said plunger, and including fixed abutment means and movable abutment means, one of said abutment means being adjustable, said abutment means being positioned to prevent movement of said speed responsive device by said spring beyond the point for which said movable abutment is adjusted, but said speed responsive device being free to move, in response to increases in speed of said engine, to separate said movable from said stationary abutment to prevent excessive speed in said engine.

6. An engine governing system including the combination of a speed responsive device, a reciprocative wedge element movable in the direction of its length by said speed responsive device upon decrease in the speed thereof, and a resilient element continuously urging said wedge in a direction opposite to that in which said wedge is moved by said device, an injector pump including a piston, resilient means urging said piston in one direction, and a reciprocative member driven from said engine and arranged to actuate said piston in the other direction, a normally stationary stop member arranged to be moved by movement of said wedge in a direction transverse to the length of said wedge, said wedge having a degree of taper such that forces transmitted in said transverse direction are prevented by friction from exerting pressure in the direction of the length of said Wedge, said stop being arranged to limit the stroke of said piston produced by said resilient means, whereby to determine the stroke of said piston produced by said reciprocative member.

'7. An engine governing system including the combination with a fuel injection pump having a plunger arranged to inject fuel upon movement in one direction, of a reciprocating member driven from said engine and arranged to actuate said plunger in said direction, a resilient element arranged to urge said plunger in the opposite direction, a speed responsive device driven by said engine, a stop member, normally stationary but arranged to be moved by the action of said speed responsive device, said member being positioned to limit the amount of movement of said plunger caused by said resilient element, a wedge element, connected with said stop member, and movable to move said stop member in a direction to reduce the stroke of said plunger caused by said resilient element, means continuously urging said wedge in such direction, an abutment connected with said wedge, a movable element arranged to contact said abutment, and connections from said speed responsive device to said movable element arranged upon response thereof to reductions in the speed of said device and engine, to move said element, and accordingly said abutment and said wedge in opposition to said means, said speed responsive device being free to move said element away from said abutment in a direction corresponding to that in which said means urges said wedge without moving said wedge, in the event of momentary resistance to movement of said Wedge by said plunger.

JOHN LEONARD TAYLOR. 

